EP0346371B1 - A heat exchanger arrangement for cooling a machine - Google Patents
A heat exchanger arrangement for cooling a machine Download PDFInfo
- Publication number
- EP0346371B1 EP0346371B1 EP88901966A EP88901966A EP0346371B1 EP 0346371 B1 EP0346371 B1 EP 0346371B1 EP 88901966 A EP88901966 A EP 88901966A EP 88901966 A EP88901966 A EP 88901966A EP 0346371 B1 EP0346371 B1 EP 0346371B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- chamber
- housing
- heat exchanger
- machine
- liquid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 13
- 239000007788 liquid Substances 0.000 claims abstract description 37
- 238000005192 partition Methods 0.000 claims abstract description 15
- 239000002826 coolant Substances 0.000 claims abstract description 13
- 239000012530 fluid Substances 0.000 claims description 4
- 239000000314 lubricant Substances 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 abstract description 6
- 238000002485 combustion reaction Methods 0.000 abstract description 2
- 230000001050 lubricating effect Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 5
- 238000010276 construction Methods 0.000 description 3
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N39/00—Arrangements for conditioning of lubricants in the lubricating system
- F16N39/02—Arrangements for conditioning of lubricants in the lubricating system by cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/0004—Oilsumps
- F01M2011/0058—Fastening to the transmission
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
- F16H57/0417—Heat exchangers adapted or integrated in the gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S165/00—Heat exchange
- Y10S165/916—Oil cooler
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2186—Gear casings
- Y10T74/2189—Cooling
Definitions
- the present invention relates to a heat-exchange arrangement for cooling a machine.
- the term machine is used in the present context as a collective designation for machines or machine assemblies of the kind which include a housing in which movable components which are driven when the machine is working are housed and which encloses a liquid medium, normally a lubricant or hydraulic fluid.
- machines of this kind include internal combustion engines, gear assemblies, automatic gear-boxes, mechanical and hydraulic clutches, other kinds of transmission elements, hydraulic pumps, hydraulic motors, compressors, etc.
- DE-B-1127668 An arrangement for cooling a liquid medium in a housing is disclosed in DE-B-1127668.
- the arrangement includes a heat exchanger which is arranged in the external wall of the housing and which comprises an outer chamber located outwardly of a partition wall in the heat exchanger.
- the outer chamber is intended to be through-passed by cooling air.
- machines lack the provision of a pump for driving the enclosed liquid medium to be cooled, or in those cases where a pump is fitted, the pump has other primary duties to fulfill and cannot therefore satisfy the requirements of the heat exchanger with regard to pressure and volumetric flow of the liquid concerned.
- One example in this respect includes the automatic gear boxes of automotive vehicles, in which the primary purpose of the pump provided is to supply the hydraulic transmission system with the requisite pressure and the requisite flow of fluid.
- the development of machines of the above-mentioned kind is also directed towards machines of progressively higher power and of more compact construction, and consequently of smaller volume, or bulk, and smaller surface areas. As a result the machines will have low inherent cooling abilities. Examples of this are motor vehicle transmission components, where the need, e.g.
- the object of the present invention is therefore to provide a heat exchanger arrangement for cooling machines of the aforementioned kind which is of simple and inexpensive construction and the function of which does not require the provision of a separate pump for moving the liquid medium to be cooled through the heat exchanger, but which will nevertheless afford a very high heat exchange effect and therewith effective cooling.
- Figures 1 and 3 illustrate very schematically and by way of example one conceivable embodiment of the invention.
- Figure 1 is a schematic sectional view of a machine of the aforedescribed kind which includes a housing 1 in which movable mechanical elements 2 are housed, these elements being driven when the machine is working, and which includes a liquid medium 3, such as a lubricant or hydraulic fluid. Since the actual construction of the machine is not relevant to the present invention, there is no need to describe the machine in detail, and hence the machine is only illustrated schematically and in principle.
- the machine may, for instance, consist of a gear box or some other form of transmission component of an automotive vehicle, which gear box or transmission component includes rotating gears and shafts and also incorporates lubricating oil.
- the machine is cooled by means of an inventive heat exchanger arrangement, generally referenced 4, which is fitted in one of the external walls 5 of the machine housing 1.
- the heat exchanger arrangement 4 includes two chambers 6 and 7 which are mutually separated by a liquid-impervious partition wall 8, which forms a part of the liquid-impervious wall of the machine housing 1.
- the heat-exchange chamber 7, located inwardly of the partition wall 8, is intended to be through-passed by the liquid 3 enclosed by the housing 1 and for cooling the machine, whereas the chamber 6, located outwardly of the partition wall 8 is intended to be through-passed by a coolant, e.g. water, which is delivered to the chamber 6 through an inlet 9 and leaves through an outlet 10.
- a coolant e.g. water
- the transfer of heat between the liquid 3 and the coolant thus takes place through the liquid-impervious partition wall 8.
- the heat transfer from the liquid 3 when the liquid flows through the chamber 7 in the heat exchanger and past the partition wall 8 takes place in accordance with the heat-exchange principle taught by International Patent Application PCT/SE 84/00245, with laminar flow of the liquid 3 in the heat-exchange chamber 7.
- the inner surface of the partition wall facing the chamber 7 is provided with a large number of fins 11 which define therebetween a large number of flow channels 12 which present an elongated rectangular, slot-like cross section and which are connected in parallel with regard to the flow of liquid therethrough (c.f. Figure 3).
- the chamber 7 has an inlet 13 through which the liquid 3 enters the chamber and from which the liquid is conducted, via distribution or auxiliary channels 14 of relatively large flow area, to a very large number of narrow flow channels 12 defined by mutually adjacent fins 11. Subsequent to passing through the narrow flow channels 12, the liquid 3 is conducted through auxiliary channels or collecting channels 15 of relatively large flow areas to an outlet 16, through which the liquid leaves the chamber 7.
- the liquid flow through the channels 12 is laminar and the channels have a short length, for instance, a length of 5-20 mm. Because of the large number of flow channels present, each of which conducts a very small volumetric flow of liquid, this will afford only a small drop in pressure.
- the relatively large auxiliary channels 14, 15 do not give rise to any appreciable drop in pressure, and as a result of the very large number of narrow flow channels 12 provided there is obtained, relatively speaking, a very large total volumetric flow through the chamber 7 at a very low total pressure drop from the inlet 13 to the outlet 16.
- a very large total volumetric flow through the chamber 7 at a very low total pressure drop from the inlet 13 to the outlet 16.
- the requisite flow of liquid 3 through the chamber 7 of the heat exchanger can be achieved in the manner illustrated in Figure 1, by arranging and positioning the heat exchanger so that the inlet 13 through which the liquid 3 enters the chamber 7 is located at a higher level than the chamber outlet 16, and so that when the machine is working,the liquid 3 is transported to the higher level of the inlet 13 under the influence of the movement of the movable mechanical elements 2, e.g. as a result of the rotary movement of a rotating gear or like element.
- the resultant hydrostatic pressure differential obtained in this way between the inlet 13 and the outlet 16 is fully sufficient to drive the requisite volume of liquid through the chamber 7 of the heat exchanger. Movement of the liquid 3 through the heat exchanger is also assisted by the increase in density experienced by the liquid as it is gradually cooled during its passage through the chamber 7.
- the outwardly located heat-exchange chamber 6 through which the cooling medium flows may be configured for turbulent flow in a conventional manner, since normally there is access to a pump which is capable of producing the pressure required to drive a sufficient volume of cooling medium in general through a turbulent-flow heat-exchange chamber. Consequently, the partition wall 8 of the heat exchanger 4 may be provided with a plurality of mutually parallel fins which extends from the inlet 9 to the outlet 10 and which define therebetween a plurality of cooling medium flow channels extending from the cooling medium inlet 9 to the cooling-medium outlet 10. This enhances the heat-exchange effect between the cooling medium and the partition wall 8 in a conventional fashion. It will be understood, however, that the outer heat-exchange chamber 6 for cooling medium may also be configured for laminar flow of the cooling medium in accordance with the heat-exchange principle taught by the International Patent Application PCT/SE 84/00245.
- the liquid medium to be cooled and enclosed in the machine housing may also be driven through the inwardly located heat-exchange chamber configured for laminar flow under the influence of a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working.
- a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working.
- auxiliary channels 14, 15 in the inner heat-exchange chamber 7 configured for laminar flow of the cooling medium 3 are placed within the chamber 7 in the form of interruptions in the fins 11 which define therebetween the laminar flow channels 12.
- these auxiliary channels 14, 15, which serve as distribution and collection channels respectively may be placed in the housing wall 5 located inwardly of the chamber 7, in the manner illustrated schematically in Figure 4. This obviates the need for corresponding interruptions in the fins 11 defining the laminar flow channels 12, and hence there is obtained a greater fin length and therewith also a greater flow channel length, which results in a greater heat-exchange effect.
- the fins 11 may be broken with short slot-like interruptions, referenced 17 in Figure 4, for the purpose described in said international patent application.
Abstract
Description
- The present invention relates to a heat-exchange arrangement for cooling a machine. The term machine is used in the present context as a collective designation for machines or machine assemblies of the kind which include a housing in which movable components which are driven when the machine is working are housed and which encloses a liquid medium, normally a lubricant or hydraulic fluid. Examples of machines of this kind include internal combustion engines, gear assemblies, automatic gear-boxes, mechanical and hydraulic clutches, other kinds of transmission elements, hydraulic pumps, hydraulic motors, compressors, etc.
- In many of these machines there exists the need to cool the liquid working in the machine. One example of an arrangement for cooling a liquid medium in a housing is disclosed in DE-B-1127668. The arrangement includes a heat exchanger which is arranged in the external wall of the housing and which comprises an outer chamber located outwardly of a partition wall in the heat exchanger. The outer chamber is intended to be through-passed by cooling air.
- Conventional heat exchangers which might conceivably be considered for use to this end work with turbulent flow. When wishing to use a turbulent-flow heat exchanger which is light in weight and small in volume and yet exhibits a high heat-exchange efficiency, the heat exchanger must operate at a relatively high pressure-drop and, in may cases, with a relatively high volumetric through-flow of the enclosed liquid medium to be cooled. Consequently, a pump must be provided to produce the requisite high drop in pressure and a sufficient large volumetric flow of medium. Many of the aforementioned machines, however, lack the provision of a pump for driving the enclosed liquid medium to be cooled, or in those cases where a pump is fitted, the pump has other primary duties to fulfill and cannot therefore satisfy the requirements of the heat exchanger with regard to pressure and volumetric flow of the liquid concerned. One example in this respect includes the automatic gear boxes of automotive vehicles, in which the primary purpose of the pump provided is to supply the hydraulic transmission system with the requisite pressure and the requisite flow of fluid. The development of machines of the above-mentioned kind is also directed towards machines of progressively higher power and of more compact construction, and consequently of smaller volume, or bulk, and smaller surface areas. As a result the machines will have low inherent cooling abilities. Examples of this are motor vehicle transmission components, where the need, e.g. of cooling simple mechanical gears and gear boxes has become progressively greater. To supply such machines, which either need no pump for their main function or which incorporate a pump which produces only relatively limited pressure and only a relatively small volumetric flow, with a separate pump in order to satisfy the requirement of a conventional turbulent-flow heat exchanger to effect the desired cooling of the machine would cause considerable technical complications and add greatly to the overall costs. Because of this, machines of this kind have hitherto not normally been provided with separate cooling arrangements, and consequently it has been necessary to accept very high machine temperatures and the problems caused thereby.
- The object of the present invention is therefore to provide a heat exchanger arrangement for cooling machines of the aforementioned kind which is of simple and inexpensive construction and the function of which does not require the provision of a separate pump for moving the liquid medium to be cooled through the heat exchanger, but which will nevertheless afford a very high heat exchange effect and therewith effective cooling.
- The characteristic features of a heat exchanger arrangement constructed in accordance with the invention are set forth in the following claims.
- The invention will now be described in more detail with reference to the accompanying schematic drawings, which illustrate a number of exemplifying embodiments of the invention and in which
- Figure 1 is a sectional view of a first embodiment of the invention;
- Figure 2 is a sectional view of a second embodiment of the invention;
- Figure 3 is a sectional view taken on the line III-III in Figure 1; and
- Figure 4 is a sectional view of a further embodiment of the invention.
- Figures 1 and 3 illustrate very schematically and by way of example one conceivable embodiment of the invention. Figure 1 is a schematic sectional view of a machine of the aforedescribed kind which includes a
housing 1 in which movablemechanical elements 2 are housed, these elements being driven when the machine is working, and which includes aliquid medium 3, such as a lubricant or hydraulic fluid. Since the actual construction of the machine is not relevant to the present invention, there is no need to describe the machine in detail, and hence the machine is only illustrated schematically and in principle. The machine may, for instance, consist of a gear box or some other form of transmission component of an automotive vehicle, which gear box or transmission component includes rotating gears and shafts and also incorporates lubricating oil. - In accordance with the invention, the machine is cooled by means of an inventive heat exchanger arrangement, generally referenced 4, which is fitted in one of the
external walls 5 of themachine housing 1. Theheat exchanger arrangement 4 includes twochambers impervious partition wall 8, which forms a part of the liquid-impervious wall of themachine housing 1. The heat-exchange chamber 7, located inwardly of thepartition wall 8, is intended to be through-passed by theliquid 3 enclosed by thehousing 1 and for cooling the machine, whereas thechamber 6, located outwardly of thepartition wall 8 is intended to be through-passed by a coolant, e.g. water, which is delivered to thechamber 6 through aninlet 9 and leaves through anoutlet 10. The transfer of heat between theliquid 3 and the coolant thus takes place through the liquid-impervious partition wall 8. The heat transfer from theliquid 3 when the liquid flows through thechamber 7 in the heat exchanger and past thepartition wall 8 takes place in accordance with the heat-exchange principle taught by International Patent Application PCT/SE 84/00245, with laminar flow of theliquid 3 in the heat-exchange chamber 7. To this end, the inner surface of the partition wall facing thechamber 7 is provided with a large number offins 11 which define therebetween a large number offlow channels 12 which present an elongated rectangular, slot-like cross section and which are connected in parallel with regard to the flow of liquid therethrough (c.f. Figure 3). Thechamber 7 has aninlet 13 through which theliquid 3 enters the chamber and from which the liquid is conducted, via distribution orauxiliary channels 14 of relatively large flow area, to a very large number ofnarrow flow channels 12 defined by mutuallyadjacent fins 11. Subsequent to passing through thenarrow flow channels 12, theliquid 3 is conducted through auxiliary channels or collectingchannels 15 of relatively large flow areas to anoutlet 16, through which the liquid leaves thechamber 7. The liquid flow through thechannels 12 is laminar and the channels have a short length, for instance, a length of 5-20 mm. Because of the large number of flow channels present, each of which conducts a very small volumetric flow of liquid, this will afford only a small drop in pressure. The relatively largeauxiliary channels narrow flow channels 12 provided there is obtained, relatively speaking, a very large total volumetric flow through thechamber 7 at a very low total pressure drop from theinlet 13 to theoutlet 16. As a result of the relatively large total volumetric flow and the extremely good heat-exchange characteristics of a heat exchanger constructed in this manner, there is achieved a fully satisfactory heat-exchange effect without requiring the provision of a separate pump to drive theliquid 3 through thechamber 7 of the heat exchanger. Thus, the requisite flow ofliquid 3 through thechamber 7 of the heat exchanger can be achieved in the manner illustrated in Figure 1, by arranging and positioning the heat exchanger so that theinlet 13 through which theliquid 3 enters thechamber 7 is located at a higher level than thechamber outlet 16, and so that when the machine is working,theliquid 3 is transported to the higher level of theinlet 13 under the influence of the movement of the movablemechanical elements 2, e.g. as a result of the rotary movement of a rotating gear or like element. The resultant hydrostatic pressure differential obtained in this way between theinlet 13 and theoutlet 16 is fully sufficient to drive the requisite volume of liquid through thechamber 7 of the heat exchanger. Movement of theliquid 3 through the heat exchanger is also assisted by the increase in density experienced by the liquid as it is gradually cooled during its passage through thechamber 7. - The outwardly located heat-
exchange chamber 6 through which the cooling medium flows may be configured for turbulent flow in a conventional manner, since normally there is access to a pump which is capable of producing the pressure required to drive a sufficient volume of cooling medium in general through a turbulent-flow heat-exchange chamber. Consequently, thepartition wall 8 of theheat exchanger 4 may be provided with a plurality of mutually parallel fins which extends from theinlet 9 to theoutlet 10 and which define therebetween a plurality of cooling medium flow channels extending from thecooling medium inlet 9 to the cooling-medium outlet 10. This enhances the heat-exchange effect between the cooling medium and thepartition wall 8 in a conventional fashion. It will be understood, however, that the outer heat-exchange chamber 6 for cooling medium may also be configured for laminar flow of the cooling medium in accordance with the heat-exchange principle taught by the International Patent Application PCT/SE 84/00245. - The liquid medium to be cooled and enclosed in the machine housing may also be driven through the inwardly located heat-exchange chamber configured for laminar flow under the influence of a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working. One such embodiment of the invention is illustrated schematically and by way of example in Figure 2, in which the same references as those used in Figure 1 have been used to identify corresponding parts.
- In the exemplifying embodiments illustrated in Figures 1-3, the
auxiliary channels exchange chamber 7 configured for laminar flow of thecooling medium 3 are placed within thechamber 7 in the form of interruptions in thefins 11 which define therebetween thelaminar flow channels 12. Alternatively, however, theseauxiliary channels housing wall 5 located inwardly of thechamber 7, in the manner illustrated schematically in Figure 4. This obviates the need for corresponding interruptions in thefins 11 defining thelaminar flow channels 12, and hence there is obtained a greater fin length and therewith also a greater flow channel length, which results in a greater heat-exchange effect. - As described in the aforementioned international patent application, the
fins 11 may be broken with short slot-like interruptions, referenced 17 in Figure 4, for the purpose described in said international patent application.
Claims (3)
- An arrangement cooling a machine which comprises a housing (1) in which movable, mechanical elements (2), which are driven when the machine is working, are housed, and which encloses a liquid medium (3), particularly a lubricant or hydraulic fluid, and which arrangement includes a heat exchanger (4) which is arranged in a part of one external wall (5) of the housing (1) and which includes a partition wall (8) and a chamber (6) located outwardly of said partition wall (8), said chamber (6) is intended to be through-passed by a cooling medium, characterized in that the heat exchanger (4) includes two chambers (6, 7) which are mutually separated by the partition wall (8), said wall being a liquid-impervious wall and constitutes a part of the liquid-impervious wall of the housing (1); in that the chamber (7) located inwardly of the partition wall (8) is intended to be through-passed by the liquid medium (3) enclosed in the housing (1); in that the inwardly located chamber (7) incorporates a large number of flow channels (12) which are connected in parallel with regard to the flow of the liquid medium therethrough; in that the flow channels (12) have a narrow rectangular cross-sectional shape dimensioned for laminar flow of the liquid medium therethrough and are defined by fins (11) formed integrally with the partition wall (8); in that the one respective ends of the flow channels communicate with an inlet (13) to the chamber (7) via distribution channels (14), whereas the other respective ends of the flow channels communicate with an outlet (16) from the chamber (7) via collecting channels (15); and in that the heat exchanger (4) is so positioned in the housing (1) that the inlet (13) and the outlet (16) of the chamber (7) located inwardly of the partitiom wall (8) have a mutual position such that when the machine is working, the liquid medium (3) will flow through the chamber (7), from the chamber inlet (13) to the chamber outlet (16), under the influence of the movement of the mechanical elements (2) housed in said housing.
- An arrangement according to claim 1, characterized in that the inlet (13) to the chamber (7) is located on a higher lever than the outlet (16); and in that the liquid medium (3) is raised to the inlet (13) under the influence of the movement of the mechanical element (2).
- An arrangement according to claim 1, characterized in that movement of the mechanical elements (2) engenders a hydrodynamic pressure difference between the inlet (13) and the outlet (16) of said chamber (7).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT88901966T ATE80698T1 (en) | 1987-02-24 | 1988-02-18 | HEAT EXCHANGE ARRANGEMENT FOR COOLING AN ENGINE. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE8700774 | 1987-02-24 | ||
SE8700774A SE455716B (en) | 1987-02-24 | 1987-02-24 | REVOLUTION DEVICE FOR COOLING A MACHINE |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0346371A1 EP0346371A1 (en) | 1989-12-20 |
EP0346371B1 true EP0346371B1 (en) | 1992-09-16 |
Family
ID=20367651
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88901966A Expired - Lifetime EP0346371B1 (en) | 1987-02-24 | 1988-02-18 | A heat exchanger arrangement for cooling a machine |
Country Status (11)
Country | Link |
---|---|
US (1) | US5072784A (en) |
EP (1) | EP0346371B1 (en) |
JP (1) | JP2704283B2 (en) |
AT (1) | ATE80698T1 (en) |
AU (1) | AU621289B2 (en) |
BR (1) | BR8807379A (en) |
CA (1) | CA1305128C (en) |
DE (1) | DE3874730T2 (en) |
HU (1) | HU206533B (en) |
SE (1) | SE455716B (en) |
WO (1) | WO1988006678A1 (en) |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19634454A1 (en) * | 1996-08-26 | 1998-03-05 | Safematic Schmiertechnik Gmbh | Heating arrangement for oil lubrication system |
WO1999066279A2 (en) * | 1998-06-19 | 1999-12-23 | Zess Technologies, Inc. | Micro-channel heat exchanger |
US6155135A (en) * | 1998-11-23 | 2000-12-05 | American Axle & Manufacturing, Inc. | Drive unit with lubricant cooling cover |
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-
1987
- 1987-02-24 SE SE8700774A patent/SE455716B/en not_active IP Right Cessation
-
1988
- 1988-02-18 AU AU13900/88A patent/AU621289B2/en not_active Ceased
- 1988-02-18 HU HU881751A patent/HU206533B/en not_active IP Right Cessation
- 1988-02-18 BR BR888807379A patent/BR8807379A/en not_active IP Right Cessation
- 1988-02-18 EP EP88901966A patent/EP0346371B1/en not_active Expired - Lifetime
- 1988-02-18 AT AT88901966T patent/ATE80698T1/en not_active IP Right Cessation
- 1988-02-18 JP JP63502084A patent/JP2704283B2/en not_active Expired - Lifetime
- 1988-02-18 DE DE8888901966T patent/DE3874730T2/en not_active Expired - Fee Related
- 1988-02-18 WO PCT/SE1988/000071 patent/WO1988006678A1/en active IP Right Grant
- 1988-02-24 CA CA000559653A patent/CA1305128C/en not_active Expired - Lifetime
-
1990
- 1990-03-29 US US07/501,320 patent/US5072784A/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
SE8700774D0 (en) | 1987-02-24 |
US5072784A (en) | 1991-12-17 |
DE3874730D1 (en) | 1992-10-22 |
WO1988006678A1 (en) | 1988-09-07 |
CA1305128C (en) | 1992-07-14 |
BR8807379A (en) | 1990-02-13 |
HU206533B (en) | 1992-11-30 |
ATE80698T1 (en) | 1992-10-15 |
AU1390088A (en) | 1988-09-26 |
AU621289B2 (en) | 1992-03-12 |
DE3874730T2 (en) | 1993-02-04 |
HUT50517A (en) | 1990-02-28 |
SE455716B (en) | 1988-08-01 |
JP2704283B2 (en) | 1998-01-26 |
JPH01502520A (en) | 1989-08-31 |
EP0346371A1 (en) | 1989-12-20 |
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